Hydraulic tool



8 Sheets $heet 1 H. J. MANSELL HYDRAULIC TOOL March 12, 1968 Fi led May 51, 1963 1 INVENTOR. HENRY J. MANS'ELL.

- AT TORNEYS 'Marh 12, 1968 J. MANSELL 3,372,570

HYDRAULIC TOOL Filed May '51, 1965 a Sheets-Sheet 2 INVENTOR. HENRY d. MANSELL AT TORNEYS March 12, 1968 H. .1. MANSELL HYDRAULI C TOOL v 8 Sheets-Sheet 3 Filed May 31, 1963 INVENTOR. HENRY J. MANSELL ATTORNEYS March 12, 1968 H. J. MANSELL 7 3,372,570

HYDRAULI C TOOL Filed May 31, 1965 8 Sheets-Sheet 4 INVENTOR. 9 I 6 HENRY J. MANSELL ATTORNEYS March 12, 1968 H. J. MANSELL 3,372,570

HYDRAULIC TOOL 7 Filed May 31, 1963 I 8 Sheets-Sheet 5 HG. 8 I5 FIG. 9

INVENTOR. HENRY d. MANSELL p20 MMWM ATTORNEYS March 12, 1968 H. J. MANSELL 3,372,570

' HYDRAULIC TOOL Filed May 31, 1963 v 8 Sheets-Sheets INVENTOR. HENRY J. MANSELL AT TOR NEYS Margh 12, 1968 H. .1. MANSELL 3,372,570

HYDRAULIC TOOL Filed May 31, 1963 s Sheets-Sheet 7 93 94 I48 I52 I63 96 87 I54 I, ,n49 156 V462 159' I60 FIG. I3

INVENTOR. HENRY J. MANSELL FIG. l5 B v ATTORNEYS Match 12, 1968 J. MANSELL' 3,372,570

HYDRAULIC TOOL Filed May 31, 1965 a Sheets-Sheet a INVENTOR. HENRY -J. MANSELL I60 BY ATTORNEYS FIG. I8

United States Patent (Mike 3,372,570 HYDRAULIC TOOL Henry J. Mansell, 225 /2 Main St., Davison, Mich. 48423 Filed May 31, 1963, Ser. No. 284,674 26 Claims. (Cl. 72-416) This invention relates to a hydraulic tool construction and more particularly to hydraulic tools of the kind particularly adapted for use in making connections on electric utility transmission and distribution lines.

Hydraulic tools of the class to which the invention relates should be capable of splicing conductors end to end with such elfectiveness as to enable the joint tobe capable of withstanding at least 95% of the tensile strength of the conductors so joined and without adversely affecting the electrical characteristics of the conductors. Such tools also should be capable of connecting conductors end to end in nontension relationship, compressing dead end fittings, joining a wire tap to a continuous conductor, cutting a conductor without hazard to the lineman and without leaving burrs on the wire ends, and compressing various kinds of terminals on conductors. Any tool capable of performing all of the foregoing functions must be capable of exerting tremendous forces on the connectors and conductors, but not all types of connections require the application of the same amount of force to provide an acceptable connection. As a result, it has been the practice heretofore to provide a number of tools of different capacities for performing diiferent operations.

In many instances it is necessary for a workman to make use of a tool of the class to which the invention relates at a level above ground, such as atop a utility pole, for example. Consequently, the weight of the tool becomes an important consideration if aerial connections are to be made eifectively.

Another important consideration in the designing of tools of the character referred to is the amount of force that must be exerted by the operator on the tool to develop the force required for the particular operation to be performed. Heretofore, it has been difficult, if not impossible, for a manually operable tool to be capable of developing the great forces necessary to make effective connections and still keep the weight of the tool within such limits as to be usable atop a utility pole. As a result, it has been the practice heretofore to utilize remote opcratingmeans which remain at ground level to develop the necessary force for performing some operations. Such an arrangement is costly and does not fully solve the weight problem inasmuch as the workman not only must support the weight of the tool, but also must support the weight of the hose, pipe, or other means by which the force developing medium is delivered from the remote means to the operating head.

An object of this invention is to provide a manually operable hydraulic tool which is capable of performing the functions referred to heretofore.

Another object of the invention is to provide a manually operable hydraulic tool which is capable of developing tremendous forces while at the same time enabling the weight and actuating forces to be maintained within such limits as to permit manual operation of the tool anywhere.

A further object of the invention is to provide a manually operable tool of the kind referred to which is capable of exerting any selected one of a plurality of forces on a workpiece.

Another object of the invention is to provide a hydraulic compressing tool which is operable to discontinue the application of force to a workpiece when a predetermined force has been obtained, and which is pro- 3 ,372,570 Patented Mar. 12, 1968 vided with manually operable means capable of relieving the applied force at any time.

Other objects and advantages of the invention will be pointed out specifically or will become apparent from the following description when it is considered in conjunction with the appended claims and the accompanying drawings, in which:

FIGURE 1 is a fragmentary, side elevational view of a tool constructed in accordance with the invention;

FIGURE 2 is a fragmentary, top plan view of the tool;

FIGURE 3 is a fragmentary, enlarged, end elevational view of the tool;

FIGURE 4 is a view similar to FIGURE 1, but with the tool rotated through to illustrate its opposite side;

FIGURE 5 is an enlarged, longitudinal sectional view taken on the line 5-5 of FIGURE 2;

FIGURE 6 is a transverse sectional view taken on the line 6-6 of FIGURE 5;

FIGURE 7 is a sectional view taken on the line 77 of FIGURE 6;

FIGURE 8 is an enlarged sectional view taken on the line 8-8 of FIGURE 1;

FIGURE 9 is a fragmentary view similar to FIGURE 8, but illustrating certain parts of the apparatus in adjusted positions;

FIGURE 10 is a fragmentary, sectional view illustrating a detail of the apparatus; 1

FIGURE 11 is a view similar to FIGURE 7, but illustrating certain parts of the apparatus in adjusted positions;

FIGURE 12 is a view similar to FIGURE 11, but illustrating certain parts in still other adjusted positions; and

FIGURES 13-18 are diagrammatic views of hydraulic control apparatus in various positions of adjustment.

A tool constructed in accordance with the invention comprises a main, hollow body 1 having a mounting flange 2 at one end thereof and on which a clamping head 3 is mounted by removable screws 4 or the like. The head 3 comprises a generally C-shaped member 5 on which is mounted a pair of relatively movable jaw support members, one of which is shown at 6 in FIGURE 5.

The movable jaw support 6 is mounted for reciprocating movements in aligned openings 7 and 8 formed in the members 3 and 1, respectively, and is provided with a socket 9 in its outer face for reception of a post 10 that projects from the rear face of a clamping die 11. The jaw support 6 is provided with a threaded bore 12 that receives a correspondingly threaded set screw 13 which seats in an annular groove 14 formed in the post 10 so as removably to connect the jaw 11 to the jaw support 6 for conjoint movements thereof. The jaw 11 and its support 6 comprise force applying jaw means reciprocable along a path.

The jaw support at the opposite side of the clamping head 3 is substantially the same as the clamping jaw 6, but it preferably is fixed against movements. The other jaw support, however, removably supports a jaw 11a which is similar to the jaw 11 and is shaped to cooperate with the latter to perform a desired function on a workpiece (not shown) that may be received between the jaws. It will be understood that the jaws 11 and 11a may be replaced by other jaws of different shapes and sizes so as to permit the tool to perform various functions on different workpieces.

The main body 1 includes a hollow, central housing 15 having an opening 16 (see FIGURE 4) at one side thereof. Rotatably received in the opening 16 is a generally cup-shaped member 17 (see FIGURE 6) having an annular wall 18 provided with a closure disk 19 at one side thereof which projects beyond the housing 15. The member 19 is rotatably retained within the housing 15 by inner and outer snap rings 20 and 21, respectively, which are removably received in grooves formed in the inner wall surface of the housing. To the inner periphery of the annular wall 18 is secured a ratchet ring 22 having two groups of openings therein. One group of openings receives radially inwardly projecting lugs 23 formed on the annular wall 18 so as to prevent relative rotation of the ring 22 and the member 18. The openings of the other group are identified by the reference character 24 and will be referred to in more detail subsequently.

The interior of the housing is divided by a partition 25 (see FIGURE 8) in which is provided an opening 26 that is coaxial with the opening 16. A rotary operating cam device 27 has a hub 28 at one end which is rotatably received within the ring 22 and a reduced hub 29 at its other end which is journaled in the partition opening 26. The partition 25 preferably includes a boss or flange 30 surrounding the opening 26 and which engages one side of the cam device 27 so as to locate the latter within the housing 15. andminimize end play. The hub 28 is provided with a radially extending bore 31 in which are received a spring 32 and a reciprocable ratchet pawl 33, the latter being adapted to project into the openings 24 formed in the ring 22. The radially outer end of the pawl 33 is inclined as at 34 at one side thereof (see FIGURE 7-) so as to permit one wall of each opening 24 to cam the pawl 33 radially inwardly and permit rotation of the cam device 27in one direction. Relative rotation between the members 18 and 27 in the opposite direction, however, is prevented by the seating of the ratchet pawl 33 in an opening 24 in the ring 22.

The cam device 27 comprises a pair of tandem cams 35 and 36, each of which has a substantialy involute cam surface formed on its periphery. The cam surfaces preferably have a greater rise at their radially inner ends than they have at their outer ends. But for this difference the cam surfaces are truly involute. The cam surface of the cam 35 rises to a terminal edge 37 which extends substantially radially inwardly to the low point of the cam surface. The cam surface on the cam 36 rises similarly to a terminal edge 38 whence it drops along a substantially radial path to the low point of the cam. The earns 35 and 36 rotate in unison in a clockwise direction, as is viewed in FIGURE 7. The cam surface on the cam 35 is arranged to lag the cam surface of the cam 36 for a purpose thatpresently will be explained.

Means designated generally by the reference character 39 is provided for actuating the operating cam device and comprises a rockable, tubular handle 40 (see FIGURES 1 and 2) that is fixed at one end to a sleeve 41 which is pinned as at 42 to a shaft 43. The shaft 43 is journaled in spaced apart lugs 44, 44a carried on a rearwardly projecting, tubular extension 45 of the body 1. A sleeve 46 also is pinned, as at 47, to the shaft 43 for rotation with the latter, and includes an integral, rearwardly inclined lever arm 48 having an opening adjacent its free end for reception of a laterally turned stub 49 of a link 50. The opposite end of the link 50 is provided with a laterally turnedv stub 51 that is received in a tubular collar 52 formed at one end of a lever 53, The opposite end of the lever 53 is fixed to the closure plate 19 of the member 17 by means of bolts, rivets or other suitable means 54.

The construction and arrangement of the actuating means 39 is such that oscillation of the handle 40 effects oscillation of the member 19 relative to the body 1. Rocking movement of the member 19 in one direction will be transmitted via the ratchet pawl 33 to the cam device 27, whereas rocking of the member 19 in the opposite direction will effect disengagement of the pawl 33 from the ratchet ring 22 and permit relative rotation of the members 19 and 27. Any tendency on the part of the ratchet pawl 33 to stick in one of the openings 24 may be overcome by providing a number of circumferentially spaced ears 55 (FIGURES 7 and 10) on the inner wall of the housing 15 at intervals corresponding to the increments of rotation imparted to the member 27 upon a full stroke of the handle 40, and by equipping the trailing edge of the lagging cam 35 with a threaded socket 56 for the reception of a threaded plug 57 housing a spring pressed ball latch 58 that may seat in a recess 59 formed in each of the ears 55.

The tubular extension 45 to which the handle 40 is pivoted has a rear wall 60 (see FIGURES 5, 8 and 9) provided with a threaded opening in which is adjustably received the threaded end 61 of a second handle 62. A sleeve 63 may be fixed to the wall 60 by screws 64 so as to surround the threaded portion 61 of the handle to protect the interior of the extension 45 against the entry of dirt. Rotation of the handle 62 in one direction or the other will cause it to be retracted into or extended from the tubular extension 45.

The inner end of the handle 62 is provided with a disk 65 that is received in a slot 66 formed adjacent the rear end of an abutment block 67 which is slideably received in the extension 45 in spaced relation to the jaw means 6. The block 67 is adjustable longitudinally of the extension 45 in prolongation of the path of the jaw means 6 in response to rotation of the handle shaft 62, and the block is provided with a slot 68 which receives a stop screw 69 threaded into the body 1 to limit forward movement of the block 67. The handle 62 is adapted to be used in conjunction with the handle 40 to support the tool and to facilitate oscillation of the handle 40. To protect the hands of a workman, the handles 40 and 62 are covered with sleeves 70 formed of electrically insulating material.

The apparatus includes hydraulic force generating means designated generally by the reference character 71 and comprising a pair of cylinders 72 and 73, both of which are supported by the body 1 and extend rearwardly along diverging lines from the housing 15. Within the cylinder 72 is a reciprocable piston 74 (see FIGURE 7) that snugly, but slideably, engages the wall of the cylinder. The periphery of the piston may be provided with a sealing ring 75 as is conventional. The inner end of the cylinder 72 is closed by an end wall 76 that is retained in place between a pair of snap rings 77. The end wall 76 is centrally bored to accommodate a piston rod 78 having a reduced end portion 79 that extends through an opening in the piston 74. The piston rod is clamped to the piston by means of a washer 80 and a snap ring 81 that cooperate with the shoulder formed at the inner end of the reduced end portion 79 and, if desired, a sealing ring 82 may surround the rod portion 79 to provide a fluid tight seal between the piston rod and the piston. The free end of the piston rod 78 extends into the housing 15 and bears against the cam surface of the cam 35 so that rotation of the cam imparts movement to the piston rod 78 and, consequently, to the piston 74. The outer end of the cylinder 72 is closed by a disk 83 that is retained between a pair of snap rings 84. The periphery of the disk 83 isgrooved to accommodate a sealing ring 85.

The cylinder 73 includes parts similar to the parts of the cylinder 72, and corresponding parts are identified by corresponding reference characters, followed by the sufiix a.

The piston rods 78 and 78a are angularly spaced from one another to correspond to the divergence of the cylinders 72 and 73. The angular spacing of the piston rods corresponds to the lead of the cam surface of the cam 36 relative to the surface of the cam 35, so as thereby to enable the piston rods and the pistons to be displaced simultaneously upon rotation of the operating cams.

Supported by the housing '15 between the cylinders 72 and 73, is a valve housing 86 comprising a pair of hollow tubes defining valve chambers 87 and 88 arranged side by side. so as to have a common inner wall 89 (see FIG- URES 8 and 9). The inner end of the valve chamber 87 is provided with an opening 90 communicating with the interior of the housing 15. at a zone that lies generally between the cams 35 and 36. The outer end of the chamber 87 is partially closed byan annular member 91 having a central opening therein and being retained by a snap ring 92. Reciprocably mounted in the chamber 87 is a force disabling spool valve 93 having an annular groove 94 formed therein and located between two enlarged end portions 95 and 96. A number of O-ring or similar seals 97 are carried by the valve at its opposite ends.

The valve 93 includes a projection 98 that extends through the opening 90 for engagement by a cooperating actuator cam 99 forming part of the cam device 27 and lying between the cams 35 and 36. The projection 98 is biased into engagement with the actuator 99 by a compression spring 100 that reacts between the valve 93 and the closure member 91. The actuator cam has a number of cam surfaces thereon, later to be referred to in more detail, that bear successively against the post 98 upon rotation of the cam device 27 to displace the valve 93. Manual means also is provided to effect displacement of the valve and comprises a rod 101 having one end threaded into the valve 93 and extending through the spring 100, the other end of the rod extending through the annular member 91 and terminating in a finger piece 102.

Slideably mounted in the valve chamber 88 is a control spool valve 103 having an annular grove 104 formed therein between two enlarged ends. Suitable sealing rings 105 surround the valve 103 to prevent leakage of fluid around the valve. The outer end of the valve chamber 88 is closed by a disk 106 that is retained by a snap ring 107, and the valve 103 is biased away from the disk 106 by a compression spring 108 that reacts between the disk and the adjacent end of the valve. The opposite end of the valve extends into a transverse bore 109 that is closed at one end by a seal 110. The opposite end of the bore 109 is open and in communication with the interior of the extension 45 (see FIGURE 8).

Slideably mounted in the bore 109 is an operating member 111 that is operable to shift the valve 103 from the position shown in FIGURE 8 to the position shown in FIGURE 9. One end of the member 111 is beveled as at 112 and seats on the complementally beveled inner end 113 of the valve 103. The opposite end of the member 111 also is beveled as at 114 and is adapted to seat on the complementally beveled edge 115 of a notch 116 formed in the slide 67. The construction and arrangement of the parts are such that inward movement of the slide 67 from its FIGURE 8 position to its FIGURE 9 position causes the actuating member 111 to be shifted out of the notch 116, and such movement of the member 111 causes the valve 103 to be shifted longitudinally of the valve chamber 88. Once the member 111 is removed from the notch 116, the wall of the slide 67 adjacent the actuating member maintains the latter in its adjusted position. When the handle 62 is adjusted to restore the slide 67 to the position shown in FIGURE 8, the spring 108 will cause the valve 103 to exert a force on the member 111 to shift the latter and reseat it in the notch 116, thereby permitting the valve 103 to be returned to the position shown in FIGURE 8.

Supported by the body 1 and forming part of the hydraulic force transmitting means is a hydraulic force applying nam 118 comprising a cylinder 119 within which is slideably mounted a free piston 120. The outer end of the cylinder 119 is closed by a plug 121 (see FIGURE 5) which is retained between snap rings 122, and is peripherally grooved to accommodate a sealing ring 123. The piston 120 has a chamber 124 at its outer end in communication with a fluid passage or slot 124a in the side of the piston and is peripherally grooved between its ends to accommodate a sealing ring 125. At its inner end, the face of the piston is recessed to accommodate a hardened metal disk 126 which functions as a wear plate. The inner end of the cylinder wall 119 is extended into the housing 15 as at 127 so as to provide a guide for the piston 120. The construction and arrangement of the ram mechanism 118 is such that fluid introduced to the cylinder 119 between the piston 120 and the closure 6 plug 121 exerts a force on the piston tending to move it inwardly of the housing 15.

Means designated generally by the reference character 128 (FIGURE 5) is provided for transmitting and multiplying force applied by the ram 118. The force transmitting and multiplying means comprises a toggle mechanism 129 having a pair of arms 130 and 131 that are pivotally connected to one another at corresponding ends by means of a hollow pivot pin 132. The pivoted end of the ram 131 is formed as a cylinder 133 and the pivoted end of the arm 130 is bifurcated to form a pair of cylindrical ears 134 between which the cylinder 133 is received. The diameters of the ears 134 are smaller than the diameter of the sleeve 133, so as to permit the latter to bear against the wear plate 126 on the piston 120.

The free end of the toggle arm 130 is shaped to form a sphere or ball 135 that is rotatably received in a correspondingly shaped socket 136 provided at the rear end of the movable jaw support 6. The free end of the toggle anm 131 also is shaped to form a ball 137 which is retatably received in a correspondingly shaped socket 138 formed in the forward end of the movable slide block 67. Normally, i.e., during periods of inactivity of the tool the toggle mechanism 129 is in a relatively collapsed position as is indicated in FIGURE 5, but the arms 130 and 131 are capable of relative movement'to an extended position in response to inward movement of the piston 120.

Stop means 139 is provided to limit extension of the toggle mechanism 129 and to return the toggle links to their collapsed positions upon release of the application of force to the toggle mechanism. The stop means 139 comprises a pair of opposed posts 140 and 141, the post 140 having a semi-spherical head 142 that is rockably received in a correspondingly shaped seat 143 formed in the toggle arm- 131. The post 141 has a similar semispherical head 144 that is seated in a correspondingly shaped recess 145 formed in the housing 15'. The posts 140 and 141 constantly are urged apart by a spring 146 which surrounds both of the posts and reacts at its opposite ends with the heads 142 and 144.

The relative lengths of the posts 140 and 141 are so selected as to permit the posts to engage one another When the toggle links 130 and 131 have been extended to a position just short of dead center relation, thereby positively precluding swinging of the toggle links beyond dead center relation. In this connection, it is pointed out that the socket 136 in the jaw support 6 is located at a slightly different level than socket 138 in the slide block 67. By this arrangement, it is not possible to position the toggle links in dead center relation unless the pivoted end of the links are moved to such positions that the links are inclined to the axis of longitudinal movement of the jaw support 6.

The construction and arrangement of the apparatus described thus far are such that oscillation of the handle 40 effects rotation of the cam device 27 which in turn causes movement of the pistons 74, 74a of the force generating means 71 to force hydraulic fluid, under the control of the valves 93 and 103, into the cylinder 119 of the ram 118 so as to displace the piston 120 inwardly, thereby effecting extension of the toggle mechanism 129 and movement of the movable jaw 11 toward the fixed jaw 11a. To effect the desired operation, fluid conduit means is included in the apparatus to conduct the pressure fluid between the cylinders 72, 73 and 119 via the apparatus 86 to enable the latter to exert the necessary control over the flow of fluid.

The fluid conduit means includes a fitting 149 connected to the valve chamber 87 and to which is joined .a tube 150 communicating between the outer end of the cylinder 72 and the fitting. A similar conductor 151 also is joined to the fitting 149 for communication between the chamber 87 and the outer end of the cylinder 73. Both of the tubes 150 and 151 communicate with the chamber 87 through a passage 152 and the chamber 87 is in communication with the chamber 88 through a port 153 in the common wall 89. Leading from the chamber 87 and in communication with the latter through a port 148 is a pipe 154 having an enlarged head 155 in which is mounted, a ball check valve 156 that yieldably is urged into sealing relation with the pipe 154 by a spring 157 that reacts between the ball 156 and a closure plug 158 at the end of the head 155. Extending between the head 155 and the cylinder 119 is a branch tube 159 for conducting fluid from the pipe 154 to the cylinder. A second branch tube 160 is joined at one end to the head 155 and is closed at its other end by a plug 161. In communication with the tube 160 is a pipe 162 that also communicates with a passage 163 which opens into the valve chamber 87 at a point spaced from the passage 152.

In communication with the valve chamber 88 is a port 164v to which is connected a fitting 167 that is supported at the intersection of two tubes 168 and 169 that lead to the inner ends of the cylinders 72 and 73, respectively. The purposes of the various passages, ports, and pipes will be explained in the description of the operation of the apparatus.

Operation The operation of the apparatus will be described first with particular reference to FIGURES 7, 9, ll, 12, 13, 14 and 15. Assume that the handle 62 is in its inwardly adjusted position, as indicated in FIGURE 9, and that the control valve 103, therefore, is in its outwardly projected position as is indicated in FIGURES 7 and 9. Assume further that the cam device 27 is in the position indicated in FIGURE 11 and that the valve 93 is in the position there indicated with its projection 98 resting on a dwell surface 99a formed on the cam 99. In these positions of the parts, a workpiece (not shown) located between the jaws 11 and 11a is in condition to be clamped therebetween upon oscillation of the handle 40.

Upon each stroke of the handle 40 toward the handle 62, the cam device 27 will be rotated in a clockwise direction, as viewed in FIGURE 11, whereupon the earns 35 and 36 will cause the pistons 74 and 74a, respectively, to be displaced toward the outer ends of the respective cylinders 72 and 73. Hydraulic fluid in the cylinders will be discharged through the respective tubes 150 and 151 t and through the port 152 into the valve chamber 87 adjacent the groove 94 in the valve 93. In the position of the valve 93 indicated in FIGURES 11 and 13, fluid occupying the groove 94 is admitted to the pipe 154 through the port 148. Fluid is transmitted by the pipe 154 past the check valve 156. Fluid may enter the pipe 162, but cannot re-enter the valve chamber 87 inasmuch as the passage 163 is blocked by the end 96 of the valve 93. Thus, fluid must pass from the check valve 156 through the pipe 159 into the cylinder 119 so as to displace the piston 120 inwardly or toward the toggle mechanism 129. As the piston 120 is displaced inwardly,

' the toggle links 130 and 131 are extended in such manner as to move the jaw support 6 and the jaw 11 toward the jaw 11a. Thus, a clamping force will be exerted on a workpiece interposed between the jaws.

Continued oscillation of the movable handle 40 will cause the cam device 27 to rotate progressively in a clockwise direction, so as progressively to extend the toggle links 130 and 131 and exert progressively increasing forces on a workpiece located between the clamping aws.

During the rotation of the cam device 27, the projection 98 f the valve 93 is maintained by the spring 100 in engagement with the cam 99 and more specifically in engagement with the peripheral dwell surface 99a of the cam so as to maintain the valve 93 in the position shown in FIGURES 11 and 13. Upon rotation of the cam device through a predetermined number of degrees, however, the valve projection 98 engages a rise surface 99b on 8 the cam 99 which acts to shift the valve 93 toward the right, as viewed in FIGURE 12. Such shifting of the valve continues until the projection 98 reaches a second dwell area 99c formed on the cam 99, at which time the valve 93- is located in the position shown in FIGURES 12 and 14.

When the valve 93 has been shifted to its adjusted position, the only change that is effected is that the passage 153 between the valve chambers 87 and 88 is uncovered by the end 96 of the valve 93. As is shown in FIGURES l2 and 14, the position of the control valve 103 is such that the port 164 communicates with the chamber 88 in the region of the groove 104 in the valve 103, thereby permitting fluid to flow from the chamber 88 into the tubes 168 and 169. When the valve 93 has been shifted to its adjusted position, further rotation of the cam device causes the force generating pistons 74 and 74a to move toward the outer ends of their respective cylinders, but it is not desired that further displacement of the piston 120 occur. Accordingly, fiuid displaced from the cylinders 72 and 73 must be diverted from the cylinder 119 into a storage area. In the adjusted position of the valve 93, fluid from the cylinders 72 and 73 is delivered via the port 164 into the conduits 168 and 169 for discharge into the inner ends of the cylinders 72 and 73 behind the associated pistons 74 and 74a. This flow of fluid occurs even though the tubes 150 and 151 still are in communication with the tube 154 because the delivery of fluid to the inner ends of the cylinders 72 and 73 offers less resistance than the delivery of fluid to the cylinder 119. Although no additional fluid is delivered to the cylinder 119, the piston 120 remains in the position to which it has been adjusted inasmuch as the check valve 156 prevents back flow of fluid through the tube 154 and the port 163 continues to be blocked by the end 96 of the valve 93.

Upon continued rotation of the cam device 27, the pistons 74 and 74a will be projected to their extreme outer positions and the projection 98 on the valve 93 will engage a second rise surface 99d on the cam 99 which acts on the valve to displace the latter to the position shown in FIGURES 7 and 15. In this position of the valve 93, the port 148 is blocked by the end of the valve 93 and the ports 152 and 163 communicate with one another and with the port 164 via the passage 153. The fluid previously introduced to the cylinder 119 then is free to return to the outer ends of the cylinders 72 and 73 via the conduit 162, the valve housing 87 and the tubes 150 and 151. By the time the valve 93 has been shifted to the position shown in FIGURES 7 and 15, the earns 35 and 36 will have been rotated past the respective piston rods 78 and78a so as to condition the associated pistons for return movement.

Return movement of the pistons is effected by the return flow of fluid from the cylinder 119 under the influence of the spring 146 in the housing 15 which reacts on the toggle mechanism 129 to force the piston outwardly, thereby forcing fluid from the cylinder 119 to the outer ends of the cylinders 72 and 73 in the manner described, to force the pistons 74, 74a inwardly. The inward movement of the pistons 74, 74a expels fluid from the inner ends of the respective cylinders through the tubes 168 and 169 through the port 164, through the passage 153 and back to the outer ends of the cylinders via the tubes and 151. The outward movement of the piston 120 also collapses the toggle mechanism 129, resulting in movement of the movable jaw 11 away from the fixed jaw 11a, thereby releasing the clamping forces on the workpiece therebetween.

As has been indicated heretofore, apparatus constructed in accordance with the invention is capable of exerting more than a single force on a workpiece clamped between the jaws 11 and 11a. The force that is exerted on a workpiece is directly proportional to the amount of movement imparted to the toggle mechanism in a direction to extend the links 131 and 131. If it is desired to exert a greater force on a workpiece than the force exerted by the apparatus when its parts are in the positions illustrated in FIGURE 9, the handle 62 may be adjusted outwardly so as to position the parts as is indicated in FIGURE 8, wherein the operating member 111 is received in the notch 116 formed in the slide block 67 and the valve 103 assumes the position shown in FIGURES 8, 16, 17 and 18. In these positions of the parts, the initial distance between the jaws 11 and 11a will be greater than when the parts are in the FIGURE 9 position, but the jaws 11 and 11a may be replaced by other jaws of different size, if desired, so as to make it possible for the apparatus to operate on either uniform or different size workpieces.

The operation of the apparatus when the parts are in the positions indicated in FIGURES 8 and 16-18 in substantially the same as the operation previously described except that the valve 103 is located in a position in which the port 164 communicating with the lines 168 and 169 leading to the inner ends of the cylinders 72 and 73 is blocked. In this position of valve 103, rotation of the cam device 27 effects outward movement of the pistons 74- and 74a in exactly the same manner as previously has been described. When the cam device 27 has been rotated to a position in which the rise surface 99b on the cam 99 engages the projection 98 on the valve 93, the latter is shifted toward the right, as viewed in FIGURE 17, in the same manner previously described, but such movement has no effect on the course of fluid discharged from the generating cylinders inasmuch as the adjusted position of the valve 93 permits fluid to flow through the port 152, around the groove 94 in the valve 93, through the port 148 into the pipe 154, past the check valve 156 and into the cylinder 119.

All of the fluid discharged from the cylinders 72 and 73 must flow into the cylinder 119, inasmuch as the port 162 is blocked by the valve 103. As fluid is forced into the cylinder 119, the piston 120 is forced inwardly so as to extend the toggle mechanism in the manner previously described. As the toggle links move toward their maximum extended positions, they magnify the hydraulic force generated by the pistons 74, 74a and transmit it to the movable jaw 11 so as to exert tremendous clamping forces on the workpiece. Since none of the fluid discharged from the cylinders 72 and 73 is diverted from the cylinder 119, a complete revolution of the cam device 27 will cause greater inward movement of the piston 120 than was the case in the previously described operation. Consequently, the toggle mechanism 129 will be moved to a more extended position of the links with the result that a greater clamping force can be exerted on a workpiece between the two jaws when the parts are adjusted to the positrons shown in FIGURE 8 than when they are in the positions shown in FIGURE 9.

In order to prevent the formation of a vacuum of such magnitude as to interfere with the displacement of the pistons '74, 74a on their force generating strokes, each cylinder 72 and 73 is provided adjacent its inner end with a vent port 130 and a manually manipulatable valve 181 that can be adjusted to permit air or other fluid to enter the cylinders behind the respective pistons. The valves 181 must remain in their open positions until the apparatus has been restored to its initial position in order to avoid trapping fluid between the pistons and the inner discs 76, 75a, and obviously the valves must be closed prior to operating the apparatus when the valve '103 is in such position as to permit the transfer of fluid from the pressure side of the cylinders '72 and 73 to the suction side thereof.

When the cam device 27 has been rotated to a position in which the cams 3 and 36 release their respective piston rods and the projection 98' on the valve 93 has traversed the rise surface 99d, the valve 93 will be in position indicated in FIGURE 18 so as to permit the return 1G flow of the fluid from the cylinder 119 to the cylinders 72 and 73 under the force of the spring 146. The return movement of the pistons 74, 7411 will exhaust fluid from the respective cylinders through the ports 180.

If at any time during the operation of the apparatus it becomes necessary or desirable to release the forces being exerted by the clamping jaws, the tool operator may grasp the finger ring 192 that is attached to the valve 93 and pull the valve to its force releasing position, indicated in FIGURES 15 and 18, thereby enabling hydraulic fluid in the cylinder 119 to be returned to the cylinders 72 and 73 in the same manner as previously has been described.

The disclosed embodiment is representative of a presently preferred form of the invention, but is intended to be illustrative rather than definitive thereof. The invention is defined in the claims.

I claim:

1. A hydraulically actuated tool comprising a body; a movable member supported on said body; hydraulic force generating means supported by said body; force transmitting means interposed between said movable member and said force generating means operable to transmit force from the latter to said movable member for moving the latter; rotary operating means acting on said force generating means for operating the latter; and disabling means reacting between said operating means and said force generating means for disabling generation of hydraulic force by the latter in response to a predetermined rotation of said operating means.

2. The construction set forth in claim 1 including manually operable means supported by said body and operable to operate said disabling means independently of said operating means.

3. A hydraulically actuated tool comprising a body; a pair of members supported on said body, at least one of said members being movable; hydraulic force generating means supported by said body; force transmitting means interposed between said movable member and said force generating means operable to transmit force from the latter to said movable member for moving the latter; rotary operating means acting on said force generating means for operating the latter; disabling means for disabling operation of said force generating means; means mounting said disabling means for movements from an inactive position to an operative position; and means reacting between said operating means and said disabling means in response to predetermined rotation of said operating means for moving said disabling means from said inactive position to said operative position.

4. The construction set forth in claim 3 including manually operable means connected to said disabling means and operable to operate the latter independently of said operating means.

5. A hydraulically actuated tool comprising a body; a movable member supported on said body; hydraulic force generating means supported by said body and including cylinder means containing hydraulic fluid and reciprocable piston means for discharging fluid from said cylinder; operating cam means acting on said piston means and operable to move the latter in a direction to effect discharge of fluid from said cylinder means; reciprocable ram means supported by said body; fluid conduit means interconnecting said ram means and said cylinder means for conducting fluid discharged from the latter to said ram means for moving the latter in one direction; force transmitting means reacting between said ram means and said movable member operable to transmit movement of said ram means to said movable member; and disabling means mounted in said conduit means and operable by said cam means to disable movement of said ram means in said one direction and thereby limit the movement of said movable member.

6. The construction set forth in claim 5 wherein said force transmitting means comprises a toggle mechanism 1 1 movable in response to movement of said ram means in said one direction from a relatively collapsed position to a relatively extended position.

7. The construction set forth in claim 6 including yieldable means reacting between said body and said toggle mechanism and constantly biasing the latter to its said collapsed position.

8. A hydraulically actuated tool comprising a body; a movable member supported on said body; hydraulic force generating means supported by said body and comprising a pair of cylinders each containing hydraulic fluid and reciprocable piston means for discharging fluid therefrom; operating means including a pair of cams rotatably mounted in said body, each of said cams having a substantially involute cam surface, and one of said cam surfaces being engageable with the piston means of one of said cylinders and the other of said cam surfaces being engageable with the piston means of the other of said cylinders; means connected to said cams for rotating them conjointly to move said piston means relatively to said cylinders in a fluid discharging direction; reciprocable ram means supported by said body; fluid conduit means interconnecting said ram means and each of said cylinders for conducting fluid discharged from the latter to said ram means for displacing the latter in one direction; a toggle mechanism having a pair of relatively movable arms. Pivotally connected to one anot er at corresponding ends and having their other ends reacting respectively between said body and said movable member, said toggle arms normally being in a relatively collapsed position with their pivoted ends in engagement with said ram means whereby displacement of said ram means in said one direction effects relative movement of said toggle arms to a relatively extended position and consequent movement of said movable member relative to said body; control means mounted in said fluid conduit means for movement from an inactive position to an operative position in which fluid discharged from said cylinders is diverted from said ram means; and means on said cam means operable to engage said control means and move the latter from said inactive position to said operative position.

9. A hydraulically actuated tool comprising a body; at least one movable member supported on said body; hydraulic force generating means mounted on said body and including hydraulic fluid conduit means; force transmitting mea'ns reacting between said generating means and said movable member for transmitting to the latter the force generated by said generating means; valve means shiftably supported in communication with said conduit means for movement from a first position enabling the transmission of force from said generating means to said transmitting means to a second position disabling such transmission of force; operating means acting on said valve means operable to shift the latter from said first position to said second position; control valve means movably supported in communication with said conduit means for movement from a first position permitting disabling of the transmission of force by said valve means to a second position prohibiting disabling of the transmission of force thereby; and means acting on said control valve means for moving the latter from its first position to its second position.

10. The apparatus set forth in claim 9 wherein said transmitting means comprises a toggle mechanism.

11. A tool comprising a body; a force exerting member; means mounting said force exerting member on said body for reciprocating movements along a path; abutment means; means mounting said abutment means in a fixed position on said body in spaced relation to said force exerting member; collapsible and expansible force transmitting means interposed between said abutment means and said force exerting member; reciprocable force applying means supported by said body for movement in a direction laterally of said path to engage and expand said force transmitting means whereby the latter effects 12 movement of said force exerting member in one direction along said path; and rotary operating means for moving said force applying means in said direction.

12. The construction set forth in claim 11 including yieldable means reacting between said body and said force transmitting means and yieldably urging the latter to its collapsed condition.

13. The construction set forth in claim 11 including stop means engageable with said force transmitting means for limiting expansion thereof.

14. The construction set forth in claim 11 wherein the means for moving said force applying means comprises hydraulic pump means supported by said body.

15. The construction set forth in claim 14 wherein said force applying means comprises a hydraulic ram having a piston for engaging said force transmitting means and being movable in said direction by fluid pressure introduced to said ram by said pump means.

16. The construction set forth in claim 15- including disabling valve means interposed between said ram and said pump means for disabling the delivery of pressure fluid by said pump means to said ram.

17. A compression tool comprising a body; fixed jaw means supported on said body; movable jaw means supported on said body for movements along a path toward and away from said fixed jaw means; abutment means; means fixedly mounting said abutment means on said body in prolongation of said path but spaced from said movable jaw means; eollapsible and expansible force transmitting means interposed between said abutment means and said fixed jaw means; reciprocable force applying means supported by said body for movement laterally of said path in a direction to engage and expand said force transmitting means whereby the latter effects movement of said movable jaw means along said path toward said fixed jaw means; and rotary operating means for moving said force applying means in said direction.

18. The construction set forth in claim 17 wherein said force transmitting means comprises a toggle link having one end engaging said movable jaw means and its other end engaging said abutment means.

19. The construction set forth in claim 18 including yieldable means reacting between said body and said toggle link and yieldably urging the latter to its collapsed condition.

20. The construction set forth in claim 18 including stop means engageable with said toggle link for limiting expansion thereof.

21. The construction set forth in claim 18 including adjustable means connected to said abutment means and operable to adjust the latter relative to said fixed jaw means.

22. The construction set forth in claim 18 wherein the means for moving said force applying means comprises hydraulic pump means supported by said body.

23. The construction set forth in claim 22 wherein said force applying means comprises a hydraulic ram having a piston for engaging said force transmitting means and being movable in said direction by fluid pressure introduced to said ram by said pump means.

24. The construction set forth in claim 23 including disabling valve means interposed between said ram and said pump means for disabling the delivery of pressure fluid by said pump means to said ram.

25. A tool comprising a body; a force exerting member; means mounting said force exerting member on said body for reciprocating movements along a path; abutment means; means mounting said abutment means in a fixed position on said body in spaced relation to said force exerting member; collapsible and expansible force transmitting means interposed between said abutment means and said force exerting member; force applying means supported by said body for movement in a direction to engage and expand said force transmitting means whereby the latter effects movement of said force exerting 13 member in one direction along said path; means for moving said force applying means in said one direction; and adjustable means connected to said abutment means and operable to adjust the position of the latter relative to said force exerting member.

26. A compression tool comprising a body; fixed jaw means supported on said body; movable jaw means supported on said body for movements along a path toward and away from said fixed jaw means; abutment means; means fixedly mounting said abutment means on said body in prolongation of said path but spaced from said movable jaw means; collapsible and expansible toggle link force transmitting means interposed between said abutment means and said fixed jaw means with one end of said toggle link engaging said movable jaw means and the other end of said toggle link engaging said abutment means and at a dilferent level than the level of engagement of said toggle link with said movable jaw means; force applying means supported by said body for movement in a direction to engage and expand said force transmitting means whereby the latter eifects movement of said movable jaw means along said path toward said fixed jaw means; and means for moving said force applying means in said direction.

References Cited UNITED STATES PATENTS 499,739 6/1893 Hunt. 2,684,003 7/ 1954 Klingler. 2,688,231 9/1954 Northcutt. 2,729,063 1/ 1956 Hoadley. 2,766,631 10/ 1956 Van Sittert. 2,821,877 2/1958 Swanson 8115 2,887,916 5/1959 Freedom 81-15 2,968,202 1/1961 Evans et al. 8115 3,053,112 9/ 1962 Klingler.

CHARLES W. LANHAM, Primary Examiner.

MILTON S. MEHR, Examiner.

M. BALAS, G. P. CROSBY, Assistant Examiners. 

1. A HYDRAULICALLY ACTUATED TOOL COMPRISING A BODY; A MOVABLE MEMBER SUPPORTED ON SAID BODY; HYDRAULIC FORCE GENERATING MEANS SUPPORTED BY SAID BODY; FORCE TRANSMITTING MEANS INTERPOSED BETWEEN SAID MOVABLE MEMBER AND SAID FORCE GENERATING MEANS OPERABLE TO TRANSMIT FORCE FROM THE LATTER TO SAID MOVABLE MEMBER FOR MOVING THE LATTER; ROTARY OPERATING MEANS ACTING ON SAID FORCE GENERATING MEANS FOR OPERATING THE LATTER; AND DISABLING MEANS REACTING BETWEEN SAID OPERATING MEANS AND SAID FORCE GENERATING MEANS FOR DISABLING GENERATING OF HYDRAULIC FORCE BY THE LATTER IN RESPONSE TO A PREDETERMINED ROTATION OF SAID OPERATING MEANS. 